Hydraulic apparatus



7, 1949. c. E. ADAMS 2,470,086

HYDRAULIC APPARATUS Filed July 19, 1944 3 Sheets-Sheet l INVENTOR- ATTORNEY May 17, 1949.. c. E. ADAMS HYDRAULIC APPARATUS Filed July 19, 1944 SEARCH ROOM 3 Sheets-Sheet 2 INVENTOR E.Adams 912m 7! a J ATTORNEY SEARCH ROOM y 1949- c. E. ADAMS 2;470,086

' HYDRAULIC APPARATUS Filed July 19, 1944 s Sheets-Sheet 3 FIG. 1. FIG-4.

( INVENTOR Cegl] E.Adc1ms ATTORNE Patented May 17, 1949 Slifiliibh KUUM HYDRAULIC APPARATUS Cecil E. Adams, Columbus, Ohio, assignor to The Denison Engineering Company,

Columbus,

Ohio, a corporation of Ohio Application July 19, 1944, Serial No. 545,701

15 Claims.

This invention relates to fluid pressure apparatus and systems employed in the operation of such apparatus. More particularly, the invention relates to a fluid system having a source of fluid pressure, a power unit and control means for governing the admission of fluid pressure to the power unit and the latters response thereto.

One object of this invention is to provide a fluid pressure system having a power unit operated by fluid pressure, with novel control mechanism by means of which the power unit will be caused to operate continuously until the operation is manually terminated by the operator.

Another object of the invention is to provide a control mechanism for a fluid pressure operated power unit, which control mechanism is responsive to a predetermined condition in the system embodying the power unit to reverse the direction of movement of the power unit.

A further object of the invention is to provide a control mechanism for governing the flow of fluid from a pump to the power unit and from the latter, the control mechanism being responsive to the return flow of fluid, that is, from the power unit, to reverse the operation of the power unit.

A still further object is to provide a fluid pressure system with a power unit responsive to fluid pressure and a control mechanism governed by the return flow of fluid from the power unit whereby a cessation of return flow will cause a reversal of operation of the power unit.

Another object consists in providing a control mechanism having a chamber with ports communicating with a source of pressure and communicating with separate portions of a power unit and controlling mechanism in the chamber to control fluid flow between the ports to effect the operation of the power unit, means being provided to restrict fluid flow in a portion of the system whereby a fiuid pressure will be generated which may be employed to govern the operation of certain parts of the control mechanism. maintenance of the fluid pressure being dependent upon the continuation of certain conditions in the system so that if those certain conditions are not maintained, a predetermined operation of the control mechanism will occur.

Another object is to provide an automatic control mechanism for a reciprocating element which will cause the element to operate repeatedly, thus, if the element is in the form of a ram for a press and the press is performing operations on articles of a certain size and it is desired to perform the operation on an article of a difierent size, it is merely necessary to present the 2 article to the ram and the operation will be performed without requiring any adjustment of the press.

An object also is to provide a flow control mechanism for a fluid pressure operated power unit which mechanism includes a casing with a cylinder having a plurality of ports communicating therewith and movably disposing a barrel member in the cylinder, the barrel member having movable valve means by which communication may be controlled between the ports to govern the operation of the power unit, the barrel member being normally disposed in one position and moved by the power unit at a certain stage of operation thereof to another position wherein the valve means will be exposed to fluid pressure to effect a certain operation thereof, the barrel being returned to another position automatically to discontinue the application of fluid pressure to the valve means after the power unit has passed such certain stage of operation whereby said valve means will respond to another force when predetermined conditions exist in the system controlled by the mechanism.

Further objects and advantages of the present invention will be apparent from the following description, reference being had to the accompanying drawings wherein a preferred form of embodiment of the invention is clearly shown.

In the drawing:

Fig. 1 is a diagrammatic view of a hydraulic system embodying the present invention;

Fig. 2 is a vertical longitudinal sectional view taken through the mechanism for controlling the operation of the system shown in Fig. l, the control mechanism being shown in a condition to cause the power unit of the system to assume an initial or starting position;

Fig. 3 is a similar view showing the control mechanism in condition to cause the power unit to start the performance of a working stroke;

Fig. 4 is a similar view showing the control mechanism in another condition which it will assume during the performance of a working stroke by the power unit;

Fig. 5 is a detail horizontal sectional view taken on the plane indicated by the line 5-5 of Fig. 2; and

Fig. 6 is a similar view taken on the plane indicated by the line 6-6 of Fig. 2.

Fig. 7 is a detailed vertical longitudinal sectional view taken through the control mechanism, showing the parts thereof in the positions occupied at the termination of a full stroke of the ram immediately before the successive down stroke is initiated.

In carrying out the present invention, the fluid pressure system is disclosed as a hydraulic system shown in Fig. l in which there is arranged a, motor driven pump 20, a reservoir 2| for bydraulic fluid. a power unit 22 and a control mechanism 23 for governing the operation of the system. The power unit 22 selected for illustration includes a cylinder 24, a piston 25 and a ram 26 projecting from the piston through the lower end of the cylinder. The piston is slidably arranged in the cylinder, the latter being illustrated in an upright position so that the piston and ram will move vertically.

The control mechanism 23 includes a casing 21 which is provided with a cylindrical chamber 28 and a plurality of longitudinally disposed ports 3| to 35, inclusive. Port 33 constitutes the inlet or pressure chamber and it is connected by a conduit 36 with the pump 28 to receive fluid under pressure therefrom. Ports 32 and 34 constitute work chambers and these are located on either side of the inlet 33; they are connected with the lower and upper ends of the power cylinder 24 by conduits 31 and 38, respectively. Ports 3| and 35 hereinafter called outlet ports, are disposed on the opposite sides of said work ports from said inlet 33 and are connected by conduits and 4| with the reservoir 2| to complete the hydraulic circuit.

A barrel 42 is disposed for sliding movement in the chamber 28, this barrel being of tubular formation, is closed at its lower end and is provided with a cap 43 at its upper end. The barrel forms an internal cylindrical chamber 44 to slidably receive a double spool valve 45. Valve 45 includes end heads 45a. and 45b, an intermediate head 45c and upper and lower interconnecting shanks 45d and 45e. The heads closely fit the cylinder 44 and are employed to control communication through the cylinder 44 between ports 46 to 50, inclusive, formed in the wall of the barrel 42. Restricted passages H are provided in head 45b to permit limited flow of fluid to opposite sides of the head 45b. When the space between heads 45b and 450 is connected to the outlet port 3|, as shown in Fig. 2, wherein said space is connected to port 3| by passage 18, fluid can escape from below head 45!) through passages 1|. In the position shown in Fig. 2, the valve 45 has been urged to its lowermost position by a coil spring 52 disposed in socket 53 of the cap 43 and socket 54 in the upper end of valve 45.

The lower portion of the valve 45 has oppositely disposed grooves 55 formed therein, one of these grooves receiving a pin 56 projecting into the lower end of cylinder 44 from the lower portion of the barrel 42. The arrangement of this pin in the groove permits the spool valve to slide freely in the cylinder 44 but prevents rotation thereof, thus insuring communication between additional ports 51 in the barrel 42 and the lower end of the cylinder 4 4through the grooves 55.

The barrel 42 is resiliently urged by a coil spring 58 to its lowered position shown in Fig. 2. This spring 58 surrounds the lower end of the barrel and engages the bottom wall 60 of a cup 6| carried by the barrel 42 through a threaded connection 62 therewith. The upper portion of the spring 58 engages the underside of the casing 21 and the spring 58 tends to hold the barrel in its lowered position against a shoulder 63 on the cap 43. When these parts are in this position, grooves 64, formed in the barrel 42, will be in .4 registration with the outlet port 3|. The ports 41 in the barrel will be in communication with work port 32 and ports 48 will be in registration with the inlet 33 so that fluid under pressure may flow from the inlet 33 through ports 48, along flats 65 formed in the spool shank 45d and through conduit 31 to the lower end of the power cylinder 24. 4

When the control mechanism is thus disposed, the upper end of the power cylinder will be vented to the reservoir through conduit 38, work chamber 34, ports 49, the upper portion of chamber 44, ports 50, outlet port 35 and conduit 4|. Since fluid under pressure is being directed to the lower:

end of the power cylinder and the upper end thereof is connected with the reservoir, piston 25 and ram 26 will move upwardly. As they approach the upper limit of movement, a fork 66 secured to the ram and straddling a rod 61 depending from the cup 6|, will engage a collar 68 adjustably attached to the rod 61, and move the barrel 42 upwardly in opposition to the force of spring 56. The spool 45 will also be moved upwardly. This upward movement will cause the ports 41 to be moved toward their nonregistering position with ports 32 to impede the flow of fluid from inlet port 33 to the conduit 31 and simultaneously will cause port 51, in barrel 42, to be brought in communication with inlet port 33. High pressure fluid will then pass from the inlet port 33, port 51 and groove 55 to the under side of head 45b of spool 45 and since restriction is offered by the passage 1| to the flow of fluid through the head 45b, high pressure fluid, on the under side of head 451), will cause the spool to rise immediately. This pressure on the under side of the head 45b of spool 45 augments the action imparted by the fork 66 so that both the barrel and the spool are moved quickly from the positions shown in Fig. 2, to the positions shown in Fig. 3. In the positions shown in Fig. 3, ports 46 of the barrel are in communication with work port 32; these ports together with flats 68, in spool shank 45e, ports 10 and grooves 64 in barrel 42 will establish communication between work port 32 and outlet port 3|. The ports 10 are of such size as to provide only restricted communication between chambers 3| and 32. The reason for this restriction will presently be set forth.

At this time, grooves 65 in the spool will establish communication between ports 48 which are in registration with the inlet port 33, and ports 49 then in registration with work port 34. Fluid will then flow from the inlet 33 through ports 48, grooves 65, ports 49 and port 34 to conduit 38 and the upper end of the power cylinder 24. This fluid under pressure will exert a downward force on the piston 25 and since the lower end of the power cylinder 24 is in communication with reservoir 2| through conduit 31, port 32, ports 46, grooves 69, ports 18, grooves 64, port 3| and conduit 48, the piston 25 and ram 26 will move downwardly. The initial downward movement of these members will cause fork 66 to move away from collar 68 and permit spring 58 to return barrel 42 to its lower or normal position as illustrated in Fig. 4. This movement will interrupt communication between ports 51 and the inlet port 33 so that fluid under pressure cannot flow from the port 33 to the lower end of the cylinder 44. There will be a tendency at this time for the spool 45 to move downwardly due to the force of spring 52. This movement, however, will be prevented until the ram has completed its downward stroke, as will be seen hereinafter. When the parts are smith ROOM in the position shown in Fig. 4, fluid being discharged from the cylinder 24 below the piston 25 must escape through the ports 10. The restriction offered by the limited siZe of port in is such that a pressure will be generated in the chamber 44 between the lower head 45b and intermediate head 45c of spool valve 45. The pressure in chamber 44 between heads 45c and 45b is such that the fluid pressure below the head 45b will not be relieved until the working stroke of the ram is completed. The spool or shuttle valve 45 will be held in the position shown in Fig. 4 due to the differential in pressure between the pressure on the underside of head or land 45b and the top side of head or land 45a, the latter being open to the reservoir and under no pressure.

When the working stroke of the ram is completed, as for example, when it is stopped by the work being performed, fluid will no longer flow from the underside of piston 25 through the conduit 3'! and, consequently, the pressure in port 32 and in the cylinder intermediate heads 45b and 450 will be reduced, due to the release of fluid through the passages 10. When this pressure is reduced, fluid can escape from the under side of head 45b through the restricted passages 'II and the spring 53 will then return the spool 45 from the position shown in Fig. 4 to the position shown in Fig. 2. Obviously, when the barrel 42 and the spool 45 are in the position shown in Fig. 2, the cycle of operation will be completed, namely. fluid under pressure will be delivered to the under side of the piston 25 and the fluid above the piston 25 will escape through ports 34 and 35 and be returned to the tank.

One of the many advantages of the present invention lies in the delayed action effected during the period of time in which the fluid escapes from below shuttle land 45b through orifices Ti after completion of the maior portion of the downstroke of the ram 26. That is. after the ram has completed or substantially completed the major portion of its movement and is stopped or retarded to such an extent that the fluid pressure decreases in chamber 32, the application of pressure is continued on the top side of piston 25 until land 45b of shuttle valve 45 blocks port 49 so that a setting force can be applied and maintained by the ram on the work being performed thereby. In other words, after the ram reaches its lowermost position or substantially its lowermost pos tion, there will be a delay before the ram is retracted. Obviously. the time interval of th s delav may be regu ated by suitably restricting the flow by the land 45b. In the present illustrations, the interval of delay is efiected by providing several shuttle valves each having restriction H of different size and selecting the shuttle valve which insures the time delay desired.

Preferably, a rel ef valve 73 is interposed between high pressure conduit 36 and the tank 2| which opens automat cally to return fluid from conduit 36 to the tank when the pressure exceeds the highest press re desirable in the system.

It w ll be seen from the foregoin that a control mechanism has been provided which w ll cause cont nuous. repeated operation of a power unit. at least a portion of the controlling operation being governed by the return flow of fluid from the power unit to the source of supply. This method of control will cause the direction of movement of the piston 25 and ram 26 to be automatically reversed at any stage of their working stroke when an obstruction, which will stop the movement of these members, is encountered.

The control mechanism shown herein may be combined with the control mechanism shown in my application Serial Number 545,700, filed on July 19, 1944, to produce a control mechanism which will effect continuous or repeated operation of a power unit and govern the operating speed thereof particularly during the working stroke whereby the power of the unit will be maintained regardless of the rate of movement of the ram.

While the form of embodiment of the present invention as herein disclosed constitutes a pre-- ferred form, it is to be understood that other forms might be adopted, all coming within the scope of the claims which follow.

I claim:

1. Control mechanism for fluid pressure operated apparatus comprising, in combination, a body having a chamber and a plurality of ports including work ports, and inlet and outlet ports; means slidable in said chamber for movement between two positions, said means having a series of ports communicating wth the ports in said body in either position of said means, said means having an additional port communicating with said inlet in one position only of said slidable means; means tending to urge said slidable means out of the said one position; flow controlling means movable between two positions, one of said means forming a passage extending from said additional port to one end of said flow controlling means to apply fluid pressure to the latter to move said latter means into a position to establish open communica ion between a predetermined work port and said inlet and restricted communication between a second work port and an outlet, one of said means forming a restricted passage to conduct fluid from said second work port to said one end of the flow controlling means to maintain the same in the communication establishing posit on after sa d first means is moved by said urging means. the fluid being dissipated through the last-mentioned restricted passage when flow from said second work port ceases to permit said flow-controlling means to move to a position to establish communication between the second work port and the nlet and the predetermined work port and an outlet.

2. A fluid pressure system comprising, in comb nation. a source of fluid under pressure; a fluid motor having a cylinder and piston; means for controlling the operation of said motor, said means including a body having a chamber and inlet. outlet and work ports communicating therewit means connecting the inlet port with said flu d pressure source. the work ports with said flu d motor on opposite sides of said piston and the outlet ports to exhaust: means slidably dispos d in said body. said slidable means having ports continuouslycommunicat ng with the ports in said bcdv. a port communicat ng with one out et port being restricted, said slidable means ha ing an addit onal port communicating with said in et in one position only of said sl dable means: means operated by said piston to move said slidable means to such position; means tending to urge said slidable means away from such position: means slidably engaging the first ment oned slidable means to control fluid flow between the ports in said first mentioned slidable means. one of said slidable means forming a passage extending from said additional port to one end of the second mentioned slidable means: r eans tending to retain the second mentioned slidable means in a posit on to establish communication between a selected work port and said inlet and the other work port and an outlet, fluid pressure admitted through said additional port and passage to said one end of the second mentioned slidable means serving to move said second mentioned slidable means to a position to connect the selected Work port with said restricted outlet and the other work port with said inlet, one of said slidable means forming a restricted passage to conduct fluid from said selected work port to said one end of said second slidable means to retain the same in the last mentioned position.

3. Flow control mechanism comprising, in combination, a body having a chamber and inlet, outlet, and work ports, communicating therewith; a ported sleeve member disposed for movement in said chamber between two positions, certain ports in said sleeve communicating with the ports in said body in both positions of movement of said sleeve and at least one of the ports in said sleeve communicating with the inlet port in one position only of said sleeve; means tending to move said sleeve out of said one position; a spool member disposed in said sleeve for movement between two positions, said spool serving to connect certain sleeve ports in one position and other sleeve ports in the other position; resilient means tending to urge said spool toward one position of movement; and passage means in one of said members for directing fluid pressure from the port communicating with the inlet port in one position only of said sleeve to one end of said spool to move the same in opposition to said resilient means.

4. In a fluid pressure system, a source of fluid pressure. a fluid motor; means for controlling the flow of fluid from said source to said motor. said means having a body with a bore and inlet, outlet and motor ports communicating therewith; a sleeve disposed for movement in said bore, said sleeve having ports formed therein for registration with the ports in said body in all positions of movement of said sleeve, and an additional port registering with the inlet portion in one position only of said sleeve; means tending to urge said sleeve out of said one position; spool means movably disposed in said sleeve and operative in one position to direct fluid from said inlet port to said fluid motor to operate the same in one direction, said spool means being operative in another position to direct fluid from the inlet port to said fluid motor to operate the same in the reverse direction; passage means for directing fluid from said additional port against said spool to move the same to the second position; means urging said spool means toward the first position; and means actuated by said fluid motor when operating in the reverse direction to move said sleeve means to the position wherein the additional port registers with said inlet port.

5. In mechanism of he character described, a source of fluid pressure, a power cylinder, a shuttle valve for controlling the flow of pressure fluid from said source to each of the opposite ends of said cylinder alternatively and from the remaining end to exhaust, a spring tending to move said valve in one direction, means for utilizing pressure from said source momentarily to move said valve in opposition to said spring, means for restricting the exhaust flow from said cylinder to create back pressure; means for utilizing the back pressure from said power cylinder to oppose the action of said spring, and means for dissipating said back pressure when exhaust flow from said cylinder is diminished, whereby said spring shifts said valve automatically.

6. In mechanism of the character described, a source of fluid pressure, a power cylinder, a barrel valve, a shuttle valve slidable endwise within said barrel valve for controlling the flow of pressure fluid from said source to each of the opposite ends of said cylinder alternatively and from the remaining end to exhaust, a spring tending to move said shuttle valve in one direction means responsive to the movement of said barrel valve and said spring actuated shuttle valve in one direction for utilizing momentarily pressure from said source to shift said shuttle valve against the action of said spring, means for restricting the exhaust flow from said cylinder to create back pressure; means for utilizing the back pressure from said cylinder to maintain said shuttle valve in its shifted position, and means for dissipating said back pressure when exhaust flow from said cylinder is diminished.

'7. In mechanism of the character described, a source of liquid under pressure; a reversible fluid motor; a valve for controlling the flow of liquid from said source to and from said motor to govern the direction of operation thereof; means for momentarily utilizing liquid under pressure from said source to move said valve to a position to cause the operation of said motor in a certain direction; orifice means for resisting flow of liquid from said motor when operating in said certain direction to create a back pressure; means for returning said valve to a second position to cause the operation of said motor in the reverse direction and means for utilizin back pressure to hold said valve in the first-mentioned position and delay the return of said valve by said returning means until the operation of said motor in said certain direction has been terminated.

8. In a fluid pressure system, a source of fluid pressure; a reversible fluid motor; a valve for controlling the flow of fluid to and from said motor to govern the direction of operation thereof; means actuated by said motor when operatin in one direction for directing fluid pressure from said source against said valve to move the same to a position to cause the operation of said motor in a certain direction; means for restricting fluid flow from said motor while operating in said certain direction to create a back pressure; means for returning said valve to a second position to cause the operation of said motor in the reverse direction; and means for utilizing the back pressure to hold said valve in the first-mentioned position and delay the return of said valve by said returning means until the operation of said motor in said certain direction has been terminated.

9. In a fluid pressure system, a source of fluid pressure; a reversible fluid motor; a valve for controlling the flow of fluid to and from said motor to govern the direction of operation thereof; means operative in one position to direct fluid from said source into contact with said valve to move the same to a position to cause the operation of said motor in a certain direction; means tending to urge said first-named means out of said one position; means for restricting fluid from said motor while operating in said certain direction to create a back pressure; means for returning said valve to a second position to cause said motor to operate in a reverse direction; means for utilizing the back pressure to hold said valve in the first-mentioned position and delay the return of said valve for said returning means until the operation of said motor in said certain SEARQH ROOM direction has been terminated; and means actuated by said motor when operating in the reverse direction to move said first-mentioned means to said one position in opposition to said urging means.

10. In a fluid pressure system, a source of fluid pressure, a fluid motor, means for controllin the operation of said motor having a casing with inlet and exhaust ports and forward and reverse motor ports; movable valve elements in said casing operative in one position to cause fluid flow from said inlet to the reverse motor port and from the forward motor port to exhaust; means actuated by said motor during reverse movement thereof to shift one of said elements to a position to interrupt fluid flow between said inlet and reverse ports; a passage way formed by said elements, said passage way being operative in the second position of said one element to direct fluid from said inlet to the other element to move the same to a position'to cause fluid flow from said inlet to the forward motor port and from the reverse motor port to an outlet, said passage way being rendered operative before fluid flow is interrupted between said inlet and reverse ports.

11; A flow control for a liquid pressure operated system comprising, in combination, a casing member forming a chamber with a liquid inlet port, a work port adapted to be connected with liquid pressure operated mechanism and an outlet port adapted to be connected with the discharge conduit of said mechanism; a valve member disposed for movement in said chamber to control the flow of liquid from the inlet port to the work port; means in said chamber normally tending to urge said valve to a position to diminish the flow of liquid between the inlet and work port; means in said casing for restricting liquid flow from the discharge conduit to exhaust to create a back pressure, one of said members forming a restricted passage to conduct such back pressure to an end of said chamber and apply the same to an end of said valve member to oppose movement thereof by said urging means.

12. In a hydraulic system, a source of fluid pressure; a fluid motor of the piston and cylinder type, valve means for directing fluid to one end of said cylinder to cause movement of said piston in one direction, and a second valve means operated by said piston for simultaneously interrupting fluid flow to said one end of said cylinder and applying full fluid pressure from said source to shift said first valve means whereby movement of said piston in said one direction will cease and the first-mentioned valve means will be in a position to direct fluid from said source to the other end of said cylinder to cause movement of said piston in the opposite direction.

13. A hydraulic system comprising a source of fluid pressure; a power cylinder; control mechanism between said pressure source and said power cylinder said mechanism having a casing, a pair of relatively movable valve elements disposed in said casing for movement between two positions relative to said casing and to one another, said elements forming a chamber for receiving fluid pressure to effect relative movement therebetween, said elements in one relative position serving to connect said chamber with said pressure source and both ends of said power cylinder to exhaust, the admission of pressure to said chamber serving to dispose said elements in a second relative position in which a predetermined end of said power cylinder is connected with said pressure source and the other end is connected with exhaust; means for restricting fluid flow between the latter end of said power cylinder and exhaust to create a back pressure, said elements forming a. passage to conduct such back pressure to said chamber to maintain said elements in the second relative position, means for moving said elements relative to said casing to disconnect said chamber from said pressure source; and means operative upon the diminution of back pressure to move one of said elements relative to the other element and said casing to connect said predetermined end of said power cylinder with exhaust and the other end with said pressure source.

14. A hydraulic system comprising, in combination, a source of liquid pressure; a liquid pressure operated power unit; valve means for controlling the flow of liquid to said power unit and from said power unit to exhaust, said valve means being disposed for movement between first and second positions; means constantly tending to retain said valve means in the first position to cause operation of said power unit in a first direction; additional valve means for applying liquid from said source to said first-mentioned valve means to move the same to the second position to cause operation of said power unit in a second direction, said additional valve means being rendered ineffective to apply liquid from said source to said first-mentioned valve means as a result of initial operation of said power unit in said second direc tion; means for restricting liquid flow which occurs only during the operation of said power unit in said second direction to create a pressure differential; and means for applying the higher pressure of said pressure differential to said firstmentioned valve means to maintain the same in position to continue the operation of said power unit in said second direction after said additional valve means has been rendered ineffective to apply liquid from said source to said first-mentioned valve means.

15. A hydraulic system comprising, in combination, a source of liquid pressure; a liquid pressure operated power unit; valve means for controlling the flow of liquid to said power unit and from said unit to exhaust, said valve means being disposed for movement between first and second positions; means constantly tending to retain said valve means in the first position to cause operation of said power unit in a first direction; additional valve means for applying liquid from said source to said first-mentioned valve means to move the same to the second position to cause operation of said power unit in a second direction, said additional valve means being rendered ineffective to apply liquid from said source to said first-mentioned valve means as a result of initial operation of said power unit in said second direction; means for restricting liquid flow which occurs only during the operation of said power unit in said second direction to create a pressure differential; means for applying the higher pressure of said pressure differential to said first-mentioned valve means to maintain the same in position to continue the operation of said power unit in said second direction after said additional valve means has been rendered ineffective to apply liquid from source to said firstmentioned valve means; and means for equalizing the pressure differential when operation of the power unit in said second direction is discon- -tinued to permit said first-mentioned valve means to return to said first position.

- CECIL E. ADAMS.

(References on following page) REFERENCES CITED The following references are of record in the file of this patent:

UNITED STATES PATENTS Number Name Date 1,931,452 Wheeler Oct. 17, 1933 2,169,470 Miller Aug. 15, 1939 2,212,871 Wood Aug. 27, 1940 Number Number Name Date Tucker Apr. 13, 1943 Harrington Nov. 21, 1944 Stacy Jan. 16, 1945 FOREIGN PATENTS Country Date Great Britain 1924 Certificate of Correction Patent No. 2,470,086. May 17, 1949.

CECIL ADAMS It is hereby certified that error appears in the printed specification of the above numbered patent requiring correction as follows: to

Column-8, 1ine 74, claim 9, for the word for read by; V

and that the said Letters Patent should be read with this correction therein that the same may conform to the record of the case in the Patent Office.

Signed and sealed this 6th day of December, A. D. 1949.

THOMAS F. MURPHY,

Assistant Commissioner of Patents. 

